Clutch and brake mechanism



Jan. 30, 1951 LJUNGKULL 2,539,545

CLUTCH AND BRAKE MECHANISM Filed Dec. 11, 1944 6 Sheets-Sheet 1 l' W mm INVENTOR.

ROLF E. LJUNGKULL A TTORNEY 6 Sheets-Sheet 2 Jan. 30, 1951 R. E. LJUNGKULL CLUTCH AND BRAKE MECHANISM Filed Dec. 11, 1944 W n A Jan. 30, 1951 R. E. LJUNGKULL CLUTCH AND BRAKE MECHANISM 6 Sheets-Sheet 3 Filed Dec. 11, 1944 INVENTOR.

ROLF E. LJUNGKULL ATTORNEY Jan. 30, 1951 R. E. LJUNGKULL CLUTCH AND BRAKE MECHANISM 6 \SheetsSheet 4 Filed Dec. 11 1944 INVENTOR.

ROLF E. LJUNGKULL A TTORNE Y Jan. 30, 1951 R. E. LJUNGKULL CLUTCH AND BRAKE MECHANISM Filed Dec. 11, 1944 INVENTOR.

ROLF E. LJUNGKULL ATTORNEY Jan. 30, 1951 R. E. LJUNGKULL CLUTCH AND BRAKE MECHANISM 5 Sheets-Sheet 6 Filed Dec. 11, 1944 HfIVENTOR ROLF E. LJUNGKULL ATTORNEY Patented Jan. 30, 1951 CLUTCHAND BRAKE MECHANISM Rolf E. Ljungkull, St. Paul, Minn., assignor to American Hoist & Derrick 00., St. Paul, Minn., a corporation of Delaware Application December 11, 1944-, Serial No. 567,705

1 11 Claims.

This invention has relation to a material handling apparatus of the type includinga drum with cable for hoisting and/or otherpurposes.

An object of the invention is to provide a material handling apparatus which will include a drum to be rotated to cause a load to be moved, as, for example, hoisted, and anovel and improved construction and arrangement for causing the drum to be operated and controlled.

A further object is to provide a. material handling apparatus constituted as a. hoist having a-drum to be rotated which will-include mechanisms for driving and braking the drum, new and improved devices adapted to be actuated to control said mechanisms, and means at a single location adapted tobe manipulated to cause the devices selectively to be actuated.

A further object is to provide a material handling apparatus Which will include a drum to'lbe rotated, mechanism for driving and braking. the drum, devices adapted to be actuated to control the mechanisms, and a unitary means adapted to be manipulated to cause the devices selectively to be actuated.

A. further object is to provide a material handling apparatus constituted as a hoist having a drum to be rotated which will include-mechanisms for driving and for braking the drumand for retaining said drumin stationary position against the weight of a load, and anovel and improved construct-ion' and arrangement for con trolling the drum driving, brakingand retaining mechanisms thus to control operation, braking and retention of said drum.

A further object is to provide a material handling apparatus which will include a combination drum braking and clutching mechanism of novel and improved construction.

A. further object is to provide a material handling apparatus wherein will be incorporated various improved features and characteristics of construction novel both as individual entities of the material handling apparatus and in combination with each other..

And a further object is to provide a material handling apparatus which will incorporate features and characteristics of construction as hereinafter explicitly set forth.

With. the. above objects in view, aswell as others which will appear as the specification proceeds, the invention comprises the construction, arrangement andcombination of :parts as now to be fully described and as hereinafter to bespecifically claimed, it being understood that the disclosure herein is merely illustrative and intended in no way in a limiting sense, changes indetails of construction andarrangement of parts being permissible so long as within the spirit of themvention and the scope of the claims which follow.

In the accompanying, drawings forming apart of this specification,.

Fig. l is .a side elevational view of a material handling apparatus made according to the invention;

Fig. 2 is. a top plan view of the material handling apparatus of Fig. 1;

Fig. 3 is a detail sectional View, taken on line 3-3 in Fig. 2;

Fig. 4 is a detail sectional view; taken on line 4-.4 in Fig. 2;

Fig. 5 is a'detail sectional view, taken on line 5-5 in Fig. 2;

Fig. 6 is a detail sectional view, taken on line- 66 in Fig. 2;

Fig. '7 is a diagrammatic view disclosing an air system of the material handlingapparatus;

Fig. 8 is an enlarged elevational view of a dog assembly of said material handling apparatus; 7

Fig. 9 is a bottom plan view of the disclosure of Fig. 10 isan enlarged elevational view of a dog shifter assembly of the material handling apparatus;- I I Fig. 11 is a top plan view of the disclosure'of Fig. 10, parts being omitted;

Fig. 12' is a front elevational view of a valve housing of thematerial handling apparatus;

Fig. 13 is a side elevational View of the valve housing. of. Fig. 12 as it would appear fromthe left;

Fig. 14 is a sectional view, taken on line 14-44 in Fig. 13; and

Fig. 15 is a sectional view,.taken on line l5-'l 5 in Fig. 12.

With respect to the drawings and the numerals of reference thereon, I5 denotes a base structure of the material handling apparatus which supports spaced apart, upstanding bearing members I6, l6 situated at opposite sides of they base structure.

A horizontal drum shaft I1 is rotatably mounted in spaced apart bearings l8, 18 provided by the bearing members l6, l6, and said drum shaft IT has an extension portion I9 situated at the outer side of one of the bearings l 8. V

A horizontal shaft 20, in spaced, parallel relationto and at a sideof the drum shaft. I1, is rotatably mounted in spaced apart bearings 2|, 2| provided by said bearing members l6. [6.

An electric motor 22, in spaced, parallel relation 3 to said drum shaft IT and at the side of the drum shaft opposite the horizontal shaft 25, is suitably and conveniently supported upon the base structure I5.

Operation of the electric motor 22 is adapted to cause the drum shaft H to be rotated through the instrumentality of a drive ratchet-belt 23 upon a ratchet-pulley 24 fixed to the driven shaft of said electric motor and also upon a ratchet-pulley 25 fixed to an extension of the horizontal shaft 20 at the side of the apparatus adjacent the electric motor shaft, and a pinion 26 fixed to an extension of said horizontal shaft 20 at the side of said apparatus adjacent the extension portion 59 which meshes with a gear 21 fixed to said extension portion l9.

A drum 28 of the material handling apparatus is situated upon the drum shaft I! and is disposed between the bearings l8, [8. As disclosed, the drum 28 includes a hollow cylindrical portion 29 in spaced, surrounding relation to the horizontal drum shaft H, and also includes hollow hubs, denoted 30 and 3|, respectively, integral with and at the opposite ends of said hollow cylindrical portion 29. A bearing housing 32, within and rigid with the hollow hub 30, is rotatably supported upon the drum shaft [1 through the instrumentality of a bearing 33, and a bearing housing 34, within and rigid with the hollow hub 3!, is rotatably supported upon said drum shaft I! through the instrumentalit of a bearing 35. The construction and arrangement are such that the drum 28, while free to rotate upon the drum shaft I1, is fixed against movement longitudinally of said drum shaft. A pipe spacer within the drum and in spaced, surrounding relation to the drum shaft is denoted 36. As shown, the pipe spacer 36 extends between the hollow hub 30 and the bearing housing 34. Additionally, the drum 28 includes annular flange members, designated 31 and 38, respectively, which are integral with and extend outwardly from the opposite ends of the hollow cylindrical portion 29 and are in perpendicular relation to the drum shaft 51. The annular flange member 31 integrally supports a cylindrical clutch drum 39 which is at the outer side of said annular flange member 37 and is concentric to the drum shaft I1, and the annular flange member 38 integrally supports a cylindrical clutch drum 40 which is at the outer side of said annular flange member 38 and is concentric to said drum shaft ll. The periphery of the annular flange member 38 is disposed exteriorly of the cylindrical clutch drum 40 and is serrated, thus to be constituted as a ratchet or toothed entity 4|.

A clutch entity 42 of the material handling apparatus, splined at 43 to the drum shaft H, is situated at the outer side of the cylindrical clutch drum 40, between said cylindrical clutch drum and the adjacent bearing I8. An adjustable clutch band 44, in surrounding relation to the clutch drum 40 and adapted to be gripped to and released from said clutch drum &0, has one of its ends 45 secured, as at 46, to the clutch entity 42 and its other end 41 secured, as at 48, to an arm 49of a clutch crank 50. Said clutch crank 50 is constituted as the arm 49, a stud 5| rigid with said arm 49 and rotatably mounted in a bracket 52 upon the clutch entity 52 and an arm 53 rigid with said stud 5i. An actuator lever for the clutch crank 50 is represented at 54. One end of said actuator lever 54 is rotatably supported upon the stud 5|, and the other end of the actuator lever is pivotally connected, at 55,

4 to a reach rod 56 which extends out of and away from a chambered housing 51. A spring supporting rod 53 slidably mounted in the bracket 52 has one of its ends 59 pivotally connected to an intermediate portion of the arm 53 of the clutch crank 53, and the opposite end of said spring supporting rod 58 fixedly carries a nut held collar 60. A compression spring 8! upon the rod 58, between the bracket 52 and the collar 60, resiliently urges said arm 53 of the clutch crank toward the actuator lever 54. An adjusting screw 62 in the free end of the arm 53 and engaged with an intermediate portion of said actuator lever 54 is for accomplishing initial adjustment of the clutch band M in a manner which will be obvious. The chambered housing 57 is rigidly supported, as at 53, upon the clutch entity A2, and an air conveying connection 65 leads interiorly along the drum shaft ll into said chambered housing 5?. The chambered housing 5! is commonly known in the art as a brake chamber. An element (not shown) within said chambered housing 5? is adapted to be actuated in response to pressure of air, by way of the air connection 64, to cause the reach rod 56 to be moved outwardly, thus to cause the actuator lever 5 3 and the clutch crank 58 to be operated against resilient action of the compression spring SE to actuate the clutch band 4t into gripping relation with the clutch drum Q5, and said compression spring 8! is adapted to react upon relief of pressure within the chambered housing 51 to cause said clutch to release said clutch drum.

A swivel joint upon the end of the drum shaft ll adjacent the gear '21 is for the purpose of conveying air under pressure to the air connection 64, whence the air will pass to the chambered housing 5?. As shown, the swivel joint includes a cup-shape body 35 in surrounding relation to a reduced portion of said drum shaft H, a gland 56 upon said reduced portion and in closing relation to said cup-shape body, and a tubular bushing El and packing 68 within the cup-shape body and surrounding the reduced portion of the drum shaft. The construction and arrangement are such that the drum shaft ll is freely rotatable within the swivel joint. A collar upon the end of said drum shaft is denoted 69, and an annular, inwardly extending flange upon the cup-shape body 65 and riding the tubular bushing 5'? is represented Hi. Longitudinal movement of the swivel joint is restricted through the bushing 61, the packing 68 and the gland 66. The cup-shape body 65 provides a chamber H within the swivel joint in surrounding relation to the end of the drum shaft, an air connection 12 leads to the chamber TI, and the air connection 64 leads from said chamber H. Air pressure inside the cupshape body 65 serves to keep the swivel joint tight.

A brake wheel '53 of the material handling apparatus, having a hub 74 supported upon the hollow hub 30 in such manner that the drum 28 can be rotatable within the brake wheel, is situated at the outer side of the cylindrical clutch drum 39, between said cylindrical clutch drum 39 and the adjacent bearing E8. The periphery of the brake wheel 13 integrally supports a brake ring l5 which is in spaced, surrounding, concentric relation to the clutch drum 39.

An adjustable main or load brake band 16, in surrounding relation to the brake ring 15 and adapted to be gripped to and released from said brake ring, has one of it sends ll secured, as at 18, to the base structure l5 and its other end crank 82: Said-brake crank 82 is'constituted- 84-is pivotally-connected, as at'85, to a reach rod 89' whichextendsout' of and away from achambered' housing 91.- The chambered housing S-Tis rigidly-supported, asat 88, upon the base structure I5; and an-air conveying connection 89 leadstosaid chambered housing 81-. The chambered housing 81 is si'milarto thechambered housing 5"! and contains an element (not shown) adapted to be actuated in response to pressure of air, byway of the-air connection 99, to cause the reach rod 99' to be moved outwardly, A springsupporting rod 99 slidably mounted,-at 9!, in the base structure I5ihas one of its ends pivotallyconnected, at 92-,- tothe outer end'cf the arm 890i the brake crank 82; and the opposite endof-said spring supporting rod 99 fiXedlycarries-a nut held collar 93; A strong compression spring 94 upon the rod 99, between the base structure I5-and the collar 93, resiliently urges said arm 94 of the brake crank 92 toward the chambered housing 31. The construction and arrangementwill be such that the strong compression spring 94- normaily will retain the brake crank 92 in position to hold the main-brake band F9- in gripping relation to the brake ring 35 and that actuation of the reach" rod 89 in response to pressure of air within the chambered housing 9? will cause said brake crank 82 to be actuated to causes said main brake band to be released'from said brake'ring. Actuation of the reach rod 89 to release the main brake band of course will be against resilient action of the strong compression spring 94, and said strongcompression spring is adapted to react upon relief of pressure within the chambered housing 9! to cause said main brake band to be gripped against said brake ring.

An adjustable difierential clutch band 95', in surrounding relation to the clutch drum 39 and adapted to be gripped to and released from said clutch drum 39, has one of its ends 96 secured, as at 9?, to an arm 99 of a crank 99 and its other end I99 secured, as at IN, to an arm I92 ofsaidcrank 99. The crank 99 is constituted as said arms 98 and I92 and a spindle I93 rigid with said arms and rotatably mounted, as at I94, upon the brake wheel IS.

The hollow hub 39 of the drum 28 supports clutch shoes, denoted I99 and I99, respectively, which are frictionally held against said hollow hub 39. In the disclosure as made, each clutch shoe I95, I96 is of part-circular configuration, and ends of the clutch shoes at one side of the hollow hub 39 are pivotally connected, as at I91. Said clutch shoes I95 and I99 ar adjustably connected to each other at the side of said hollow hub 39 opposite the pivotal connection I9! by a headed and nutted bolt I 99, and a small compression spring I99 upon said tie bolt resiliently urges said clutch shoes I95, I99 toward each other and against the hollow'hub 39 in such manner as to permit movement of rotation of said hollow hub Within the clutch shoes but to cause said clutch shoes to be frictionally engaged against the hollow hub so that there will be tendency toward movement of rotation of the clutch shoes in the same direction as said hollow hub when the hollow hub is rotated. The outer end of an extension I I9 of the clutch shoe I99,

disposed perpendicularlyof the hollow 39, pivotall connected, as at I I I, to a link I I2 which is at substantially right angle relation to "said extension H9." The opposite endofthe IIZ- ispivotally connected, as at I9I, to the outer end of the arm-I92;

As will be'noted-in Figs'fi andd of the drawings, the spindle I93 is situated in spaced relation to the clutch'drum '39; and the arms 98 and I92 of the crank'99 aresub'stantiallyperpendicu lar to each otherand are' situated'at the side of said'spindle'opp'osite said cl'utch dru'm' 39. Itwill;

also be noted in Fig. 4 that the connection9'I is closer to the spindle I93 than is th connection I9 I. That is to say, the end 96 of the clutch band 95 is secured to the'cra'nk 99 at closer relation to said spindle I93 than is the end I99 of said clutch band. Obviously, the differential clutch: band 95 will be expanded or lengthened in response to,

rotary movement of the crank 99 as in said Fig.

4 in clockwise direction andwill'becontractedjor shoes I95, I99and the crank 99 as'in Fig.4'tobe' rotated in clockwise direction thus to cause the differential clutch band 95 to be released 'from the clutch drurn'99 andthat commencementpf rotary movement of saiddrum 29 in opposit direction under stress of a load will cause said clutch shoes I95, I96and said crank 99 as in said" Fig. 4 to be rotated in counterclockwise direction thus to cause said differential clutch band 95 to be tightly gripped to and against said' clutch drum 39. The longer ar m'I92 of the crank 9,9 will evidently apply more tension to the differential clutch band 95'than the shorter arm'98 of said crank will releaseupon rotation of the crank in counterclockwise 'directionso that sa'iddifferential clutch band will be rigidly 'gripped'against the clutch drum"39, and saidlonger arml92 will just as evidently'place more slack in saiddifferential clutch band than 'said'shorter arm 98'w'ill remove upon rotation of said'crank in clockwise direction so that the diiferential clutch band will be released from said clutch drum.

An adjusting screw H5" in an extension I I6of the arm 98 of the crank 99 and adapted'to'ibe' engaged against'a stop I I I provided by the brake wheel 13 is for the purpose of limiting the extent to which said crank 99 can be rotated in clock- Wise'direction. V

The material handling apparatus includes mechanism,c'onstituted as a dog I I9 adapted to be engaged with anddisengaged from the ratchet or toothed entity 4| integral with the annular and the anchor piece I2 I, is rotatably mounted,

as at I23, upon the stub shaft H9. A roller I24 is supported upon an intermediate portion of the actuator arm I22, and a tension spring I25 has one of its ends secured, as at I29, to the anchor piece I 2| and its other end, Secured as at I21 to the end of said actuator arm I22 spaced from the stub shaft H9.

A dog shifter frame I28 is suitably and conveniently supported, as at I29, upon the base structure I5, and a cam shaft I30, rotatably mounted upon said dog shifter frame, fixedly supports a cam I3I having a working surface I32 adapted to be engaged against the roller I24. A ratchet I33 upon the cam shaft I33 is adapted to be advanced through the instrumentality of an actuator pawl I34 and retained at advanced position by a check pawl I35. The actuator pawl I34 is rotatably mounted, as at I36, upon and between actuator plates I31 themselves rotatably supported upon the cam shaft I33. A small tension spring I38, connected to the actuator plates I31 and to the actuator pawl I34, resiliently urges said actuator pawl into engagement with the ratchet I33. The check pawl I35 is rotatably mounted upon the dog shifter frame I28, and a small tension spring I39, connected to said frame I28 and to the check pawl, resiliently urges said check pawl into engagement with said ratchet I33. A portion of each actuator plate I31 spaced from the actuator pawl I34 is pivotally connected, as at I40, to a reach rod I4I which extends out of and away from a chambered housing I42. The chambered housing I42 is rigidly supported, as at I43, upon the dog shifter frame I28, and an air conveying connection I44 leads to said chambered housing I42. The chambered housing I42 is similar to the chambered housings 51 and 81 and contains an element (not shown) adapted to be actuated in response to pressure of air, by way of the air connection I 44, to cause the reach rod I M to be moved outwardly thus to cause the actuator plates I 31 and the actuator pawl I34 to be operated to advance the ratchet I33. A stop element I45 upon the reach rod I 4| is adapted to be engaged against the cam shaft I30 thus to limit and control the extent to which said ratchet I33, and, hence, the cam I3I, is advanced for each outward movement or actuation of said reach rod MI. The construction and arrangement will be such that the reach rod I4I will be returned to normal receded position upon release of pressure within the chambered housing I42, thus to cause the actuator pawl I34 to be returned to normal receded position, as will be obvious.

As disclosed, the cam I3I is of generally triangular shape, and the working surface I32 of said cam includes three apices each of curvilinear configuration and spaced at I25 degrees apart and three flat surfaces between the apices. The construction and arrangement will be such that the roller I24 alternately will be adjacent the apices and flat surfaces of said working surface I32 of the cam I3I. Supposing said roller I24 to be adjacent to a fiat surface of said cam I3I, actuation of the reach rod MI in response to pressure of air will cause the cam to be advanced to extent causing an apex of said cam to move or swing the roller I24 and the actuator arm I22 toward the dog H8 and away from the anchor piece I 2I thus to move or swing said dog H8 into engagement with a tooth of the ratchet 4i under resilient action of the tension spring I25, and supposing the roller I 24 to be against an apex of the cam I 3I, actuation of said reach rod MI in response to pressure of air will cause said cam to be advanced to extent causing a side of the cam to be adjacent said roller I24 thus to permit the dos M8 to be kicked out and clear of the ratchet or toothed entity M in response to slight rotation of the drum 28 in load lifting direction. Stated otherwise, operation of the reach rod MI in response to air pressure while the dog H8 is released from the ratchet or toothed entity M will cause said dog to be set against said ratchet or toothed entity, and operation of said reach rod MI in response to air pressure while the dog H8 is set against the ratchet or toothed entity will situate the cam I3I in position adapted to permit release of said dog from said ratchet or toothed entity.

An air conveying connection I43 leads from a source (not shown) of air under pressure to a valve housing I41, and each of the air conveying connections 12, 89 and I44 leads from said valve housing. A three-way valve I49 in the valve housing I41, controlled by a manually actuable lever I48, is adapted selectively to control passage of air from the air connection I46 by way of said three-Way valve to each of said air connections 12, 89 and I44, respectively. In Figs. 7, l3 and 14 of the drawings, the manually actuable control lever I48 is disclosed in neutral position, or position precluding flow of air from the air connection I45 to each and all of the air connections 12, 89 and I44.

When it is desired that the drum 28 be driven by the electric motor 22, the control lever I48 is operated to position the valve I43 to open the air connection I46 having air under pressure to the air connection 12, thusto cause air under pressure to be applied, by way of the chamber 1| and the air connection 64, to the chambered housing 51. Pressure of air in said chambered housing 51 will force the reach rod 53 outwardly and cause the clutch band 44 to be gripped to the clutch drum 43 in the manner as hereinbefore set forth. The drive of said drum will be through the drum shaft I1, the spline 43, the clutch entity 42, the clutch band 44 and the clutch drum 43. The drum 28 will be driven in direction to cause the differential clutch band to be released from the clutch drum 33 in the manner as has been explained so that said differential clutch band 35 will offer no interference to rotation of said drum 28 when rotated to elevate or pull in a load. When it is intended that driving of the drum 23 be terminated, said control lever I48 is operated to position the valve I49 to shut off the air connection I46 from the air connection 12, thus to cause pressure within the chambered housing 51 to be relieved. The clutch band 44 will at once become released from the clutch drum 40 upon relief of pressure within said chambered housing 51 so that the drum 28 will, if under the weight, of a load, have tendency to turn in direction opposite the direction in which said drum is driven. Immediately, however, the clutch shoes I95, I33 will rotate in direction causing the differential clutch band 95 to be gripped to the clutch drum 33, and inasmuch as the main or load brake band 16 is normally gripped to the brake ring 15 upon the brake wheel 13, rotation of the drum in direction counter to its driving direction will be terminated substantially concurrently with release of said clutch band 44 from said clutch drum 40. Stated otherwise, said drum 23 will be retained in stationary position against the weight of a load upon release of the clutch entity 42 from the drum by the main or load brake band 16 when set, the brake ring 15, the brake wheel 13, the differenti-al clutch band 95 and the clutch drum 39.

When it is desired that a load be paid out. Q1.

housing 8'I.

lowered, the control lever H48 is operatedto position'the valve I49 to open the air connection I46 to the air connection 89, thus to cause air under pressure to be applied to the chambered Pressure of air in said'chambered housing 81 will force the reachrod 'BG-outwardly and cause the main orload brake band iii to be released from the brake ring 15 in the manner which has'been explained. When it is intended that pay out, or lowering, of the load be terminated, said control lever I48 is operated to position the valve I49 to shut ofi" the air connection I46 from the air connection'ii thus to cause pressure within the chambered housingB? to be relieved. The main or load brake band it will at once become gripped to the brake ring '15 upon relief of pressure within said chambered housing 81, and the drum 28 will, if under the weight of a load, have tendency tocont'inue to turn in paying out, or lowering, direction.

The clutch shoes I05, Iilfi, however, will be rotated'during pay out, or lowering, of a load in direction to pay out, or lowering, of the load by reason of the fact that the differential clutch band '95 will have become gripped against the clutch drum 39 while the load was being paid out, or lowered. Actually, in practical operation, the differential clutch band 95 becomes grip ed to the clutch drum'3e whenever a load is held by the main or load brake'band'lfi, and paying out, or lowering, operations have tendency to actuatesaid difierential clutch toward its gripping position rather than toward its releasedposition.

When it is intended that the dog H8 be engaged with the ratchet or toothed entity 4| to cause the drum 28 to be "retained'instatiOnary position against the Weight of a load, the control lever I48 is operated to position the valve I49 to open the air connection I46 to the air connection I44, thus to cause air under pressure te'be applied to the chambered housing I42. Pressure of air in said chambered housing I42 will force the reach rod I4! outwardly and cause said dog I I8'to be applied to said ratchet or toothed entity 4! in the manner as hereinbefore set forth. Upon operation of said control lever 1143 to po sition the valve 549 to shut off the air connection I46 from the-air connection I44tocause pressure within the chambered'housing I42 to be'relieved after the dog I I8 has been setagainst the ratchet or toothed entity 4!, the reach rod I4I will recede thus to cause the actuator pawl N24 to be returned to normal receded position. When it is intended that the actuating mechanism for the dog II8 be set to permit said dog to be kicked out and clear of the ratchet or toothed entity 4| in response to slight rotation of the drum 28 in load lifting direction, the control lever M3 is also operated to position the valve I453 to open the air connection E46 to the air connection 544, thus to cause air under pressure to be applied at the chambered housing I42 to force the reach rod I4I to move outwardly and advance said actuating mechanism in the manner as hereinbefore explained. Upon operation of said control lever I48 to position the valve I49 to shut off the air connection Hi6 from the air connection -44 to cause pressure within said chambered housing 10 142' to be relieved after the actuating mechanism for the dog H8 has been situated topermit kicking of said dog out and clear of said ratchet or toothed entity 4|, the reach rod will recede and cause the actuator pawl to be returned to normal recededposition.

What is claimed is:

1. In material handling apparatus, the combination with a rotatably supported main-drum of a drum braking and clutching mechanism comprising a clutch drum rigid with said main drum, a brakewheel rotatably supported upon said main drum, a brake ring rigid with said brake wheel, a brake'band, means for causing said brake band to be engagedwith and released from said brake ring, and a differential clutch band supported by said'brake wheel and adapted to be engaged with and released from said clutch drum.

In material handling apparatus, the combinationwith a rotatably supported main'drum of adrum braking andclutching mechanism comprising a clutch drum rigid with said main drum, a brake wheel rotatably supported upon said main drum, a brake ring rigid with said brake wheel, a brake band, means for actuating said brake band into engaged relation with and released relation from said brake ring, and a differential clutch band in surrounding relation to 'said clutch drum and having its opposite ends supported upon said brake wheel, said differential clutch band being adapted to 'grippingly engage s'aid clutch drum in response to rotation of said main drum relative to said brake wheel in one direction and to become released from said clutch drum in response to rotation of said main drum relative to said brake wheel in opposite direction.

3. In material handling apparatus, the combination with a rotatably supported main drum of a drum braking and clutchin mechanism comprising a clutch drum rigid with said main drum, a brake'wheel rotatably supported upon said main drum, a brake-ring rigid with said brake wheel, a brake band in surrounding relation to said brake ring, means for actuating said brake band into engaged relation with and released from said brake ring, a crank having an intermediate portion thereof rotatably mounted upon said brake wheel at the-outer-sideof said clutch drum and including spaced apart, outwardly "extending arms, a differential clutch band in surrounding relation to saidclutch drum and having its opposite-ends connected to-the spaced apart arms,

respectively, of saidcrank at unequal distances from the crankmounting, an'element rotatably and frictionally supported'by said-main drum, and

a link between said element and an arm of said crank.

4. In material handling apparatus, the combination with a drum shaft and a main drum rotatably supported upon said drum shaft, of mechanism for driving said main drum including a first clutch drum rigid with said main drum, a clutch entity fixed to rotate with said drum shaft and a clutch band supported by said clutch entity in surrounding relation to the first clutch drum and adapted to be engaged with and released from said first clutch drum, a drum braking and clutching mechanism comprising a second clutch drum rigid with said main drum, a brake wheel rotatably supported upon said main drum, a brake ring rigid with said brake wheel, a brake band, means for causing said brake band to be engaged with and released from said brake ring and a differential clutch band supported by said brake 11 wheel and adapted to be engaged with and released from said second clutch drum.

5. In material handling apparatus, the combination with a drum shaft'and a main drum rotatably supported upon said drum shaft, of mechanism for driving said main drum including a first clutch drum rigid with said main drum, a clutch entity fixed to rotate with said drum shaft and a clutch band supported by said clutch entity in surrounding relation to the first clutch drum and adapted to be engaged with and released from said first clutch drum, a drum brakin and clutching mechanism comprising a second clutch drum rigid with said main drum, a brake wheel rotatably supported upon said main drum, a brake ring rigid with said brake wheel, a brake band, means for actuating said brake band into engaged relation with and released relation from said brake ring and a differential clutch band in surrounding relation to said second clutch drum and having its opposite ends supported upon said brake wheel, said differential clutch band being adapted to grippingly engage said second clutch drum in response to rotation of said main drum relative to said brake wheel in one direction and to become released from said second clutch drum in response to rotation of said main drum relative to said brake wheel in opposite direction.

6. In material handling apparatus, the com-- bination with a drum shaft and a main drum rotatably supported upon said drum shaft, of mechanism for driving said main drum including a first clutch drum rigid with said main drum, a clutch entity fixed to rotate with said drum shaft and a clutch band supported by said clutch entity in surrounding relation to the first clutch drum and adapted to be engaged with and released from said first clutch drum, a drum braking and clutching mechanism comprising a second clutch drum rigid with said main drum, a brake wheel rotatably supported upon said main drum, a brake ring rigid with said brake wheel, a brake band in surrounding relation to said brake ring, means for actuating said brake band into engaged relation with and released relation from said brake ring, a crank having an intermediate portion thereof rotatably mounted upon said brake wheel at the outer side of said second clutch drum and including spaced apart, outwardl extending arms, a diiferential clutch band in surrounding relation to said second clutch drum and having its opposite ends connected to the spaced apart arms, respectively, of said crank at unequal distances from the crank mounting, an element rotatably and frictionally supported by said main drum and a link between said element and an arm of said crank.

7. The combination as specified in claim 4, a ratchet fixed to rotate with said main drum, and

means adapted to be engaged with and disengaged from said ratchet to retain the main drum in stationary position against the weight of a load and release said main drum to said load.

8. The combination as specified in claim 5, a ratchet fixed to rotate with said main drum, and means adapted to be engaged with and disengaged from said ratchet to retain the main drum in stationary position against the weight of a load and release said main drum to said load.

9. The combination as specified in claim 6, a

ratchet fixed to rotate with said main drum, and means adapted to be engaged with and disengaged from said ratchet to retain the main drum in stationary position against the weight of a load and release said main drum to said load.

10. In material handling apparatus, a drum to be rotated, first mechanism for driving said drum in a given direction, a brake wheel rotatably mounted on said drum, second mechanism for clutching said brake wheel to said drum when the drum rotates under the weight of a load in direction opposite its driven direction and for unclutching said wheel when said drum is being driven by said first mechanism, third mechanism operable upon said brake wheel for braking said drum and retaining the drum in stationary position against the weight of the load, devices adapted to be hydraulically actuated to control said drum driving, braking and retaining mecha nisms, and means adapted to be manipulated at a single location for causing said devices selectively to be actuated.

11. The combination as specified in claim 10, a ratchet fixed to rotate with said drum, and means adapted to be engaged with and disengaged from said ratchet to retain the drum in stationary position against the weight of a load and release said drum to said load.

ROLF E. LJUNGKULL.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 53,621 Hoyt Apr. 3, 1866 248,286 Bruner Oct. 18, 1881 312,146 Merritt Feb. 10, 1885 661,070 Olds Nov. 6, 1900 840,223 Laidlaw et al. Jan. 1, 1907 1,298,956 Johnson Apr. 1, 1919 1,707,219 Cook Apr. 2, 1929 1,805,482 Dyrr May 19, 1931 1,864,126 Ferris June 21, 1932 2,185,551 Glasner Jan. 2, 1940 2,366,433 Bridwell et al Jan. 2, 1945 

